CN104411988B - Fluid dynamic bearing device and motor with same - Google Patents

Fluid dynamic bearing device and motor with same Download PDF

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Publication number
CN104411988B
CN104411988B CN201380031745.8A CN201380031745A CN104411988B CN 104411988 B CN104411988 B CN 104411988B CN 201380031745 A CN201380031745 A CN 201380031745A CN 104411988 B CN104411988 B CN 104411988B
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China
Prior art keywords
bearings
parts
bearing
gap
axial
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CN201380031745.8A
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CN104411988A (en
Inventor
小松原慎治
栗村哲弥
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NTN Corp
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NTN Corp
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
    • F16C17/107—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one surface for radial load and at least one surface for axial load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/02—Sliding-contact bearings
    • F16C25/04—Sliding-contact bearings self-adjusting
    • F16C25/045—Sliding-contact bearings self-adjusting with magnetic means to preload the bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
    • F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
    • F16C32/0651—Details of the bearing area per se
    • F16C32/0659—Details of the bearing area per se of pockets or grooves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/107—Grooves for generating pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/74—Sealings of sliding-contact bearings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/46—Fans, e.g. ventilators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2370/00—Apparatus relating to physics, e.g. instruments
    • F16C2370/12—Hard disk drives or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/103—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing
    • F16C33/104—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing in a porous body, e.g. oil impregnated sintered sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1085—Channels or passages to recirculate the liquid in the bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C43/00—Assembling bearings
    • F16C43/02—Assembling sliding-contact bearings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Power Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Sealing Of Bearings (AREA)

Abstract

A fluid dynamic bearing device is provided with: a rotation-side bearing member consisting of a porous material; a stationary-side housing having the bearing member received at the inner periphery thereof; a seal member for opening the upper side of the bearing member to the atmosphere through a seal gap; a radial bearing gap formed between the outer peripheral surface of the bearing member and the inner peripheral surface of the housing; and a thrust bearing gap formed between the lower end surface of the bearing member and the inner bottom surface of the housing. The radial bearing gap and the thrust bearing gap are filled with lubricating oil, and oil films formed in both bearing gaps support the bearing member in the radial direction and in the thrust direction. An axial gap which contains air is disposed between the upper end surface of the bearing member and the lower end surface of the seal member, the lower end surface facing the upper end surface.

Description

Fluid dynamic-pressure bearing device and the motor possessing this fluid dynamic-pressure bearing device
Technical field
The present invention relates to a kind of fluid dynamic-pressure bearing device and the motor possessing this fluid dynamic-pressure bearing device.
Background technology
It is known that fluid dynamic-pressure bearing device has the features such as high-speed rotation, high running accuracy and low noise.Cause This, fluid dynamic-pressure bearing device is suitable as being equipped on the axle of the motor of various electrical equipments with information equipment as representative Bearing apparatus and use, specifically, the spindle drive motor being suitable as being assembled in the disc driving means such as HDD is used, is assembled in PC Use Deng fan motor or be assembled in bearing arrangement of polygon scanner motor of laser printer (LBP) etc. and make With.
Fluid dynamic-pressure bearing device possess the radial bearing portion in radial directions part of rotary side being supported, The thrust bearing division in thrust direction, the part of rotary side being supported, in recent years, in order to effectively play These characteristics, warp To constitute radial bearing portion and thrust bearing division both sides usually through hydrodynamic bearing.As this fluid dynamic-pressure bearing device, carry Go out various devices, such as, in Fig. 2 of patent documentation 1, disclose a kind of following fluid dynamic-pressure bearing device, described fluid Hydrodynamic bearing apparatus possess the parts of bearings of sintering metal of composition rotary side, parts of bearings are contained in inner circumferential ground Stationary side Housing, and be formed between the outer peripheral face in parts of bearings and the inner peripheral surface of housing between the journal bearing of radial bearing portion Gap.In addition, in this fluid dynamic-pressure bearing device, thrust axis is formed respectively by the end face and other end of parts of bearings The thrust bearing gap of bearing portion.
According to the structure of patent documentation 1, with the outer peripheral face in axle portion part and the parts of bearings of the inner circumferential being fixed on housing The structure (for example, patent documentation 2) in journal bearing gap forming radial bearing portion between inner peripheral surface is compared, except being capable of footpath Additionally it is possible to act on the centrifugation of lubricating oil by the rotation with parts of bearings beyond increasing to the bearing area of bearing portion Power, and using lubricious lubricating oil come full of journal bearing gap.Therefore, at the aspect of the bearing value improving radial bearing portion And stably maintain radial bearing portion bearing value aspect favourable.
Citation
Patent documentation
Patent documentation 1：Japanese Unexamined Patent Publication 2007-24089 publication
Patent documentation 2：Japanese Unexamined Patent Publication 2003-336636 publication
Content of the invention
Invention problem to be solved
However, fluid dynamic-pressure bearing device as described in Patent Document 1 is like that, by the end face of parts of bearings with And in the case that other end forms thrust bearing gap respectively, in order to prevent the rupture of oil film in two thrust bearing gaps, need With lubricating oil come the inner space full of housing.Above-mentioned conclusion obtains according to following content, i.e. enter in the peristome to housing The pasta (with reference to the paragraph 0028 of patent documentation 1) of lubricating oil is kept in the range of the seal clearance of row sealing.
However, when the above configuration is adopted, after the assembling of bearing arrangement, need loaded down with trivial details using so-called vacuum infiltration etc. Method to be full of the inner space of housing using lubricating oil, and need the pasta of lubricating oil is accurately managed (section is finely adjusted to lubricants capacity).Accordingly, there exist and be difficult to tackle the further cost degradation for fluid dynamic-pressure bearing device Requirement problem.
Therefore, it is an object of the invention to provide a kind of can be manufactured with low cost and can play desired bearing The fluid dynamic-pressure bearing device of performance.
Means for solving the problems
The present invention implementing to realize above-mentioned purpose is a kind of fluid dynamic-pressure bearing device, the bearing portion of rotary side Part, it is formed by porous material, and has end face in axial both sides；The housing of Stationary side, it is in that axial side is closed There is bottom tube-like, parts of bearings is contained in inner circumferential；Seal member, it is opposed with the end face of the axial opposite side of parts of bearings to join Put, make the axial opposite side of parts of bearings via seal clearance to atmosphere opening；Journal bearing gap, it is formed at parts of bearings Outer peripheral face and the inner peripheral surface of housing between；Thrust bearing gap, it is formed at the end face of axial side of parts of bearings and shell Between the inner bottom surface of body, journal bearing gap and thrust bearing gap are full of by lubricating oil, by being formed at journal bearing gap Respectively parts of bearings is supported in radial direction and thrust direction one side with the oil film in thrust bearing gap, described fluid Hydrodynamic bearing apparatus are characterised by, in the end face of the axial opposite side of parts of bearings and the end face of the seal member opposed with it Between be folded with the axial gap containing air, the external force producing in the outside of housing act on parts of bearings and by parts of bearings Press on axial side, thus supporting to parts of bearings on thrust direction the opposing party.
In fluid dynamic-pressure bearing device (below, also referred to as " bearing arrangement ") involved in the present invention, above-mentioned Under the situation that journal bearing gap and thrust bearing gap are full of by lubricating oil, in the end face of the axial opposite side of parts of bearings It is folded with the axial gap containing air and the end face of the seal member opposed with it between.That is, represent under the above conditions, energy Enough pastas keeping lubricating oil in the range of axial gap, in this case, can make to be filled in the inner space of housing The volume of the inner space than housing for the lubricants capacity (with two bearings gap as representative, is formed at the appearance in the gap between two parts Long-pending summation) little.Thus, after assembling this bearing arrangement, even if executing for example using the fuel feeding instrument such as micropipette from close It is also possible to there is requirement in the inner space of housing in this simple operation of inner space oiling sealing gap to housing Lubricating oil, therefore, there is no need to high-precision pasta regulation management operation, thus enable that the manufacturing cost of bearing arrangement Cheaper.
In said structure, can act on parts of bearings has the external force that parts of bearings presses on axial side.This Sample one, can support to parts of bearings on thrust direction two direction.Therefore, it is possible to be avoided as much as following situation, That is, the load bearing capacity being formed at thrust direction one side of the oil film in thrust bearing gap is excessive, is accompanied by this, leads to thrust The support accuracy destabilization in direction.In addition, it is another to support thrust direction in the thrust bearing division by being made up of hydrodynamic bearing In the structure of patent documentation 1 of the load of one side, need high-precision to the gap width in the thrust bearing gap of this thrust bearing division It is adjusted managing degree, but it is not necessary to this adjust management operation in the structure of the invention described above.Accordingly, it is capable to Enough realize the cost degradation of this bearing arrangement, and improve bearing performance.
For example above-mentioned external force can be given by magnetic force.For instance, it is possible to by being in staggered configuration in the axial direction, be arranged on will be static Stator coil that the housing of side is held on the holding member (motor base) of inner circumferential, it is arranged on the parts of bearings of rotary side Rotor magnet giving this magnetic force.That is, described external force is the magnetic force producing between stator coil and rotor magnet, described fixed Subcoil is arranged at the Stationary side including housing, and described rotor magnet is arranged at the rotary side including parts of bearings.It is being assembled with In the various motor of this fluid dynamic-pressure bearing device, usually as necessary component parts, possess rotor magnet and stator Coil.Therefore, if adopting said structure, can give above-mentioned in the case of not leading to larger cost to increase at low cost External force.
In said structure, can also have press-in portion, described press-in portion is when parts of bearings rotates by axial gap Lubricating oil to radially away from seal clearance direction press-in.So, the rotation of parts of bearings can be prevented as much as possible The oil leak via seal clearance of (in the operating of bearing arrangement) and the fall of consequent bearing performance in turning Low.
Press-in portion for example can be formed from forming multiple groove portion structures of at least one party in opposed two faces of axial gap Become, but in view of the good processability of the parts of bearings being formed by porous material, preferably, be formed from parts of bearings Multiple groove portions of the end face of axial opposite side are constituted.
It is preferably, the well width constituting each groove portion of press-in portion gradually subtracts towards the direction radially away from seal clearance Little.By capillary attraction, easily keep the lubricating oil in axial gap in the position radially away from seal clearance, therefore Favourable in terms of preventing via the oil leak of seal clearance.Additionally, it is preferred that being, each groove portion constituting press-in portion is formed as groove Width is with the section shape being gradually reduced towards bottom land side.By capillary attraction, can be by the profit in axial gap Lubricating oil imports to the bottom land side (axially away from side of seal clearance) of each groove portion, is therefore preventing the profit via seal clearance Lubrication leakage aspect is advantageously.
In above structure, seal clearance can be formed at the outer peripheral face of axle portion part and seal member inner peripheral surface it Between, the periphery of described axle portion part is fixed with parts of bearings, the inner peripheral surface of described seal member and housing one or split setting.? In the case of being somebody's turn to do, journal bearing gap can be formed at and lean at outside diameter than seal clearance.Therefore, if be made up of multiple groove portions Press-in portion, and so that the well width of each groove portion is gradually reduced towards the direction radially away from seal clearance, then can be in bearing Both sides when part stops and during rotation, all easily will be located in the lubricating oil of axial gap and import to journal bearing gap.By This, be full of journal bearing gap by lubricious lubricating oil, be capable of the stabilisation of the running accuracy of radial direction.
In above structure, can be outside the inner peripheral surface of the housing opposed via journal bearing gap with parts of bearings Either one or both in side face is provided for the dynamic pressure generating section making the lubricating oil in journal bearing gap produce dynamic pressure effect (radial dynamic pressure generating unit).
It is preferably, radial dynamic pressure generating unit is to thrust when parts of bearings rotates by the lubricating oil in journal bearing gap The shape that bearing clearance side pressure enters.This is due to can prevent the rupture of oil film in thrust bearing gap as much as possible, thus real The stabilisation of the running accuracy of existing thrust direction one side.
The access making the both ends of the surface of parts of bearings connect can be arranged on parts of bearings.By arranging this connection Road, can make to be located in the lubricating oil energetically flow circuit of the inner space of housing, therefore can in the operating of bearing arrangement Enough it is effectively prevented because of the pressure balanced collapse within bearing arrangement, the lubrication shortage of oil of each bearing clearance and the bearing that causes The reduction of performance.
Fluid dynamic-pressure bearing device involved in the present invention illustrated above has various feature illustrated above, therefore It is suitable in the various motor such as fan motor, the spindle drive motor of disc driving means of such as PC to be assembled in Use, and can aid in the cost degradation of various motor.
Invention effect
To sum up, in accordance with the invention it is possible to offer is a kind of with low cost manufacture and can play desired bearing The fluid dynamic-pressure bearing device of performance.
Brief description
Fig. 1 is the sectional view of the configuration example schematically showing fan motor.
Fig. 2 is the sectional view of the fluid dynamic-pressure bearing device involved by the first embodiment representing the present invention.
Fig. 3 is the top view of the lower surface representing the parts of bearings shown in Fig. 2.
Fig. 4 is the top view of the upper surface representing the parts of bearings shown in Fig. 2.
Fig. 5 a is the X1-X1 regarding sectional view in Fig. 4, and for representing the one of the groove portion of upper surface being arranged at parts of bearings The figure of individual example.
Fig. 5 b is the sectional view of the variation of the groove portion representing the upper surface being arranged at parts of bearings.
Fig. 5 c is the sectional view of the variation of the groove portion representing the upper surface being arranged at parts of bearings.
Fig. 6 is the top view of the upper surface of the parts of bearings representing variation.
Fig. 7 is the sectional view representing the fluid dynamic-pressure bearing device involved by second embodiment of the present invention.
Fig. 8 is the sectional view representing the fluid dynamic-pressure bearing device involved by third embodiment of the present invention.
Specific embodiment
Hereinafter, with reference to the accompanying drawings embodiments of the present invention are illustrated.
Schematically show the fan motor being assembled with fluid dynamic-pressure bearing device 1 involved in the present invention in FIG A configuration example.Fan motor shown in this figure possesses：Fluid dynamic-pressure bearing device 1, the work of the Stationary side of composition motor The stator coil 5 for the motor base 6 of holding member, being installed on motor base 6, the conduct with blade (omitting diagram) The rotor 3 of rotary part, it is installed on rotor 3 gap on the radial direction rotor magnet opposed with stator coil 54. The housing 7 of fluid dynamic-pressure bearing device 1 is fixed on the inner circumferential of motor base 6, and rotor 3 is fixed on fluid dynamic-pressure bearing device 1 Axle portion part 21 one end.In such fan motor constituting, when be energized to stator coil 5, by stator coil 5 and Electromagnetic force between rotor magnet 4 makes rotor magnet 4 rotate, and is accompanied by this, and possesses axle portion part 21, is fixed on the tool of axle portion part 21 Vaned rotor 3 and be fixed on the rotary body 2 of the rotor magnet 4 of rotor 3 etc. and rotate.
It should be noted that when rotary body 2 rotates, the form according to the blade being arranged at rotor 3 and towards in figure Side or lower section air-supply.Therefore, in the rotary course of rotary body 2, as the counteracting force of this air-supply effect, in fluid dynamic pressure shaft The axle portion part 21 of bearing apparatus 1 and effect on the parts of bearings 22 of its periphery of being fixed on have pushing away towards in figure below or above Power.Between stator coil 5 and rotor magnet 4 effect have offset this thrust direction magnetic force (repulsion), because above-mentioned thrust with The difference of the size of magnetic force and the thrust load that produces is supported by the thrust bearing division T of fluid dynamic-pressure bearing device 1.Above-mentioned counteracting pushes away The magnetic force in the direction of power for example can produce and (omit in detail by being in staggered configuration stator coil 5 and rotor magnet 4 in the axial direction Thin diagram).In addition, when rotary body 2 rotates, on the axle portion part 21 and parts of bearings 22 of fluid dynamic-pressure bearing device 1 Effect has radial load.This radial load is supported by radial bearing portion R of fluid dynamic-pressure bearing device 1.
Figure 2 illustrates the fluid dynamic-pressure bearing device 1 involved by the first embodiment of the present invention.This fluid dynamic pressure shaft Bearing apparatus 1 possess as main component parts：Constitute the axle portion part 21 of rotary side and the bearing portion being fixed on its periphery Part 22, there is bottom tube-like and parts of bearings 22 and axle portion part 21 are contained in the Stationary side of inner circumferential in what axial side was closed Housing 7 arranged opposite with the end face of the axial opposite side of parts of bearings 22 and by the axial opposite side of parts of bearings 22 via close The envelope seal member 9 to atmosphere opening for the gap S.It is filled with lubricating oil 11 (to be cutd open with intensive distribution in the inner space of housing 7 Upper thread represents), in the state of fig. 2, at least journal bearing gap of radial bearing portion R and pushing away of thrust bearing division T Power bearing clearance is full of by lubricating oil 11.It should be noted that following, for convenience of description, the one of seal member 9 will be configured with Side is set to upside, and its axial opposition side is set to downside.
Housing 7 has bottom tube-like in the bottom 7b's of lower ending opening with cylindric cylinder portion 7a and closing cylinder portion 7a, Here, cylinder portion 7a and bottom 7b is formed by metal or resin.The inner peripheral surface of cylinder portion 7a is divided into greatly by end difference Footpath inner peripheral surface 7a1 and path inner peripheral surface 7a2, is fixed with seal member 9 on big footpath inner peripheral surface 7a1.Path inner peripheral surface 7a2 with There is between the outer peripheral face 22a of the parts of bearings 22 being fixed on axle portion part 21 cylindrical region forming journal bearing gap, should Cylindrical region is formed as there is not concavo-convex even surface.In addition, the inner bottom surface 7b1 of bottom 7b is in the lower end with parts of bearings 22 There is between the 22c of face the area forming thrust bearing gap, this area is formed as there is not concavo-convex smoothing Face.
Seal member 9 is circular by metal or resin formation, and by suitable sides such as bonding, press-in, press-in bondings Method and be fixed on the big footpath inner peripheral surface 7a1 of housing 7.Outer in the inner peripheral surface 9a of seal member 9 and the axle portion part 21 opposed with it It is formed with seal clearance (labyrinth sealing) S, the upside of parts of bearings 22 is opened to air via seal clearance S between side face 21a Put.
Axle portion part 21 is formed by stainless steel and other metal materials, and its outer peripheral face 21a is formed as smooth barrel surface.In axle portion part 21 upper end periphery is fixed with the vaned rotor 3 of tool.
Parts of bearings 22 is by porous plastid, here by with the metal of copper (inclusion copper series alloy) or ferrum (inclusion iron-based alloy) Powder is that the porous plastid of the sintering metal of main component is formed as cylindric.Beyond parts of bearings 22 can also be by sintering metal Porous plastid, such as Porous resin formation.This parts of bearings 22 is located at the lower surface with axle portion part 21 with lower surface 22c 21b compares the mode by axially external (downside), by press-in, bonding, press-in bonding (simultaneously using press-in and bonding), welding It is fixed on the outer peripheral face 21a of axle portion 21 etc. suitable method.
Parts of bearings 22 possesses one or more access 8 making its both ends of the surface 22b, 22c connect.Here, as Fig. 3 and Shown in Fig. 4, by being formed at axial groove 22dl, the axle portion part in smooth cylinder planar of the inner peripheral surface 22d of parts of bearings 22 21 outer peripheral face 21a forms access 8.It is of course also possible to axial groove being arranged by the outer peripheral face 21a in axle portion part 21 and being formed Access 8.
It is provided with for shape between the path inner peripheral surface 7a2 of opposed housing 7 in the outer peripheral face 22a of parts of bearings 22 The radially radial bearing surface of the cylindrical shape of bearing clearance.It is formed with for making the profit in journal bearing gap in radial bearing surface Lubricating oil 11 produces dynamic pressure generating section (radial dynamic pressure generating unit) A of dynamic pressure effect.Radial dynamic pressure generating unit A is passed through will be mutually to phase Opposite direction tilts and detached in the axial direction multiple dynamic pressure groove Aa1, Ab1 are constituted so that chevron shape arranges.Produce in radial dynamic pressure In life portion A, the axial dimension of the axial dimension of the dynamic pressure groove Aa1 of the upside dynamic pressure groove Ab1 than downside is big.Thus, in rotary body 2 During (axle portion part 21 and parts of bearings 22) rotation, the lubricating oil 11 being full of in journal bearing gap is by (thrust downward The thrust bearing clearance side of bearing portion T) press-in.
It should be noted that each dynamic pressure groove constituting radial dynamic pressure generating unit A for example can shape parts of bearings 22 Simultaneously (specifically, by the bearing material enforcement pressure-sizing processing to the cylindrical shape that metal dust press-powder sinters Shape finishing size shape parts of bearings 22 while) contour forming, in view of the good processability of sintering metal, The plastic workings such as rolling can be implemented by outer peripheral face is configured to the bearing material of even surface and be formed.In addition, radial dynamic pressure The generation type of generating unit A (dynamic pressure groove) is not limited to this.For example, radial dynamic pressure generating unit A can also along the circumferential direction be arranged Arrange multiple spiral-shaped dynamic pressure grooves.
As shown in figure 3, being provided with the inner bottom surface 7b1 with opposed housing 7 in the lower surface 22c of parts of bearings 22 Between formed thrust bearing division T the ring-type in thrust bearing gap thrust bearing surface.This thrust bearing surface is provided with use Lubricating oil 11 in thrust bearing gap is made to produce pushing away of dynamic pressure effect in rotating with axle portion part 21 and parts of bearings 22 Power dynamic pressure generating section B.Thrust dynamic pressure generating unit B by circumferentially arranging multiple spiral-shaped dynamic pressure groove Ba at predetermined intervals and Constitute, and have the lubricating oil 11 in thrust bearing gap in the rotation of axle portion part 21 and parts of bearings 22 to internal side diameter Be pressed into pumps into function.Thrust dynamic pressure generating unit B can also be by circumferentially configuring the dynamic pressure groove of chevron shape at predetermined intervals And constitute.
Be provided between the upper surface 22b and the lower surface 9b of the seal member 9 opposed with it of parts of bearings 22 containing The axial gap (annulus) 10 of air.Fluid dynamic-pressure bearing device 1 (will be close in the state being configured with the attitude shown in Fig. 2 Envelope gap S is configured at the state on the upside of vertical direction) under, at least journal bearing gap of radial bearing portion R1, R2 and thrust The thrust bearing gap of bearing portion T is full of by lubricating oil 11, and the pasta being filled in the lubricating oil 11 of the inner space of housing 7 keeps In the range of above-mentioned axial gap 10.
Therefore, in this fluid dynamic-pressure bearing device 1, it is filled in the amount (body of the lubricating oil 11 of the inner space of housing 7 Long-pending) less than the volume of the inner space of housing 7.
The upper surface 22b of parts of bearings 22 is provided with press-in portion 12, this press-in portion 12 is in axle portion part 21 and bearing portion During the rotation of part 22, by the lubricating oil 11 in axial gap 10 to the direction radially away from seal clearance S (in present embodiment In be radially oriented outside) press-in.As shown in figure 4, press-in portion 12 is made up of the multiple groove portions 13 circumferentially configuring at predetermined intervals, Here constitutes each groove portion 13 by the radiation groove radially extending.Each groove portion 13 is in its well width with towards outside diameter (radially Leave the direction of seal clearance S) form that is gradually reduced, and there is its well width be gradually reduced with towards bottom land side Section shape.It should be noted that as the section shape of each groove portion 13, such as removing can be using the section triangle shown in Fig. 5 a Additionally it is possible to adopt the section trapezoidal shape shown in Fig. 5 b or the section semi-circular shape shown in Fig. 5 c beyond shape.
The upper end periphery chamfered edge 22e of the external diameter end of each groove portion 13 and inner diameter end parts of bearings 22 and upper end inner circumferential Respectively opening on chamfered edge 22f, the groove depth of groove portion 13 is set as less than the chamfer amount of upper end periphery chamfered edge 22e.For example, will be upper In the case that the chamfer amount of end periphery chamfered edge 22e is set to 0.2mm, the groove depth of groove portion 13 is set as 0.15mm.This be by In when the groove depth of groove portion 13 is bigger than the chamfer amount of upper end periphery chamfered edge 22e, there is the outer peripheral face being formed at parts of bearings 22 The shape of radial dynamic pressure generating unit A (the dynamic pressure groove Aa1 on the upside of particularly) of 22a is destroyed, the supporting energy to radial bearing portion R The probability that power adversely affects.
The dynamic pressure groove Ba of lower surface 22c and upper surface 22b and the groove portion 13 that are respectively arranged at parts of bearings 22 are permissible (specifically, implement in the bearing material by sintering to metal dust press-powder while shaping parts of bearings 22 While pressure-sizing processes parts of bearings 22 that shape goes out polish geomery) contour forming, in view of sintering metal is good Processability it is also possible to the plastic working such as punching press being implemented by the bearing material that both ends of the surface are configured to even surface and being formed.
Possess the fluid dynamic-pressure bearing device 1 of above structure for example to complete by following operation, i.e. by axle portion part 21 with And the parts of bearings 22 being fixed on the periphery of this axle portion part 21 is inserted into the inner circumferential of housing 7, seal member 9 is being fixed on housing After 7 big footpath inner peripheral surface 7al, filled out to the inner space of housing 7 via seal clearance S using the fuel feeding instrument such as micropipette Fill (injection) lubricating oil 11.
In the fluid dynamic-pressure bearing device 1 being made up of above structure, when axle portion part 21 and parts of bearings 22 rotate, It is being arranged between the radial bearing surface of outer peripheral face 22a of parts of bearings 22 and the path inner peripheral surface 7a2 of the housing 7 opposed with it It is formed with journal bearing gap.And, with the rotation of axle portion part 21 and parts of bearings 22, it is formed at journal bearing gap Oil film pressure improves because the dynamic pressure of radial dynamic pressure generating unit A acts on, and forms countershaft part 21 and bearing in radial directions Part 22 carries out radial bearing portion R of noncontact supporting.
Meanwhile, in the thrust bearing surface of the lower surface 22c being arranged at parts of bearings 22 and the housing 7 opposed with it It is formed with thrust bearing gap between inner bottom surface 7b1.And, with the rotation of axle portion part 21 and parts of bearings 22, thrust axis The oil film pressure holding gap improves because the dynamic pressure of thrust dynamic pressure generating unit B acts on, and forms part countershaft to thrust direction one side 21 and parts of bearings 22 carry out the thrust bearing division T of noncontact supporting (floating supporting upward).It should be noted that as joined As illustrated by Fig. 1, acting on axle portion part 21 and parts of bearings 22 has as the external force pressing downwards them Magnetic force, thus, suppression axle portion part 21 and parts of bearings 22 excessive floating.
As described above, when axle portion part 2 and parts of bearings 22 rotate, the lubricating oil 11 in journal bearing gap is downward Side is pressed into.Thus, when parts of bearings 22 rotates, between the outer peripheral face 22a and the inner peripheral surface 7a2 of housing 7 of parts of bearings 22 Gap in the lubricating oil 11 of sandwiched flow downwards, in the thrust bearing gap of thrust bearing division T → be arranged at parts of bearings The path of the axial gap 10 between the upper surface 22b of 22 access 8 → parts of bearings 22 and the lower surface 9b of seal member 9 Middle circulation, and be directed into again in the journal bearing gap of radial bearing portion R.Particularly, in the present embodiment, thrust dynamic pressure Generating unit B has and for the lubricating oil 11 in thrust bearing gap to pump into function to what internal diameter side pressure entered, and in parts of bearings 22 Upper surface 22b setting there is the press-in portion 12 pumping out function entering the lubricating oil 11 in axial gap 10 to external diameter side pressure (multiple groove portion 13), therefore promotes the flow circuit of lubricating oil 11 further.By using this structure, due to ensureing While the pressure balance of the inner space of housing 7, prevent journal bearing gap and the thrust bearing division T of radial bearing portion R Thrust bearing gap in rupture of oil film, therefore, it is possible to realize the stabilisation of bearing performance.
As shown above, in fluid dynamic-pressure bearing device 1 involved in the present invention, in journal bearing gap and thrust Under (Fig. 2) under the situation that bearing clearance is full of by lubricating oil 11, in upper surface 22b and the sealing opposed with it of parts of bearings 22 Between the lower surface 9b of part 9, it is folded with the axial gap 10 containing air.That is, represent under the above conditions, can be in axial direction Keep the pasta of lubricating oil 11 in the range of gap 10, in this case, the profit being filled in the inner space of housing 7 can be made The volume of the inner space than housing 7 for the amount of lubricating oil 11 (with two bearings gap as representative, is formed at gap between two parts The summation of the volume of the internal voids of parts of bearings 22 of volume and sintering metal) little.Thus, assembling this bearing dress After putting 1, though execution for example using the fuel feeding instrument such as micropipette from seal clearance S to the inner space oiling of housing 7 this Plant simple operation it is also possible to there is the lubricating oil 11 of requirement in the inner space of housing 7, thus without high accuracy Pasta management.
In addition, act on having that on parts of bearings 22 parts of bearings 22 is pressed (the opposing party supports by thrust direction) downwards External force.So, due to can support to parts of bearings 22 on thrust direction two direction, therefore, it is possible to as far as possible Avoid following situation, i.e. the load bearing capacity being formed at thrust direction one side of the oil film in thrust bearing gap is excessive, companion With in this, lead to support accuracy (running accuracy) destabilization of thrust direction.In the present embodiment, given by magnetic force Above-mentioned external force, and by configuring setting on the motor base 6 be held in the housing 7 of Stationary side inner circumferential vertically with staggering Stator coil 5, be arranged at rotary side parts of bearings 22 rotor magnet 4, to give this magnetic force.It is being assembled with this fluid In the various motor of Hydrodynamic bearing apparatus 1, as necessary component parts, possess rotor magnet 4 and stator coil 5.Therefore, If adopting said structure, larger cost can not be led to increase and give above-mentioned external force at low cost.
It should be noted that by the pasta keeping lubricating oil 11 in axial gap 10, can be solid by seal member 9 Carried out the oiling operation of the inner space to housing 7 before housing 7.So, with warp after the fixation of seal member 9 The situation filling lubricating oil 11 to the inner space of housing 7 from seal clearance S is compared, and can simplify oiling operation.
For the structure of fluid dynamic-pressure bearing device 1 involved in the present invention, for example by with shown in Fig. 2 in the way of upper and lower The attitude of upset uses this bearing arrangement 1 in this case, the probability meeting that lubricating oil 11 spills to outside via seal clearance S Slightly improve.For this problem, as described above, can be effectively prevented by following measure, i.e. (1) arrange press-in portion 12, This press-in portion 12 when axle portion part 21 and parts of bearings 22 rotate, by the lubricating oil 11 in axial gap 10 to radially away from Direction (in the present embodiment for the outside diameter) press-in of seal clearance S；(2) by the upper surface 22a being arranged at parts of bearings 22 Multiple groove portions 13 constitute press-in portion 12, and make the well width of each groove portion 13 towards the direction radially away from seal clearance S And be gradually reduced；And each groove portion 13 constituting press-in portion 12 is formed as making well width with towards bottom land side gradually by (3) Section shape reducing etc..
That is, if adopting above-mentioned (2), by capillary attraction, can be easily in the position radially away from seal clearance S Put the lubricating oil 11 in place's holding axial gap 10, if in addition adopting above-mentioned (3), by capillary attraction, can be by axle Import to the lubricating oil in gap 10 to the bottom land side (axially away from side of seal clearance S) of each groove portion 13.
It should be noted that, although omit diagram, but in order to be more effectively prevented from letting out via the lubricating oil of seal clearance S Leakage is it is also possible to set in adjacent with seal clearance S and the outer peripheral face 21a with the axle portion 21 of atmosphere, seal member 9 upper surface Put oil suction film.
In addition, if as shown in the embodiment, seal clearance S is formed in the outer peripheral face 21a of axle portion part 21 and fixation Between the inner peripheral surface 9a of the seal member 9 of housing 7, then journal bearing gap can be formed at and lean on seal clearance S-phase ratio Outside diameter.And, by aforesaid way being arranged at the upper end of parts of bearings 22 by the press-in portion 12 that multiple groove portions 13 are constituted Face 22b, in the stopping of axle portion part 2 and parts of bearings 22 and when rotating, is easy to will be present in the profit of axial gap 10 Lubricating oil 11 imports to the journal bearing gap of radial bearing portion R.Begin in journal bearing gap thereby, it is possible to make radial bearing portion R It is full of by lubricious lubricating oil 11 eventually, thus realizing the stabilisation of the running accuracy of radial direction.
More than, the fluid dynamic-pressure bearing device 1 involved by embodiments of the present invention is illustrated, but is not taking off Various changes can be implemented with each portion of convection current hydrodynamic bearing apparatus 1 in the range of the purport of the present invention.
For example, press-in portion 12 can be constituted by arranging multiple spiral-shaped groove portions 13 as shown in Figure 6.If Spiral-shaped groove portion 13, then, compared with the radial groove portion 13 shown in Fig. 4, can increase the sectional area of each groove portion 13 (volume).Therefore, it is possible to make more lubricating oil 11 sandwiched (holding) in axial gap 10, realizing bearing performance raising side Face is favourable.
In addition, as shown in fig. 7, being used for the radial axle being supported in the countershaft part of radial direction 21 and parts of bearings 22 Bearing portion can be separately provided at two positions (radial bearing portion R1, R2) in axial direction.In the figure 7, in parts of bearings 22 At two positions of the axial direction of outer peripheral face 22a, it is provided for being formed footpath between the path inner peripheral surface 7a2 of opposed housing 7 Radial bearing surface to the cylindrical shape of bearing clearance.Two radial bearing surface are respectively formed with for making journal bearing gap Interior lubricating oil 11 produces dynamic pressure generating section (radial dynamic pressure generating unit) A1, A2 of dynamic pressure effect.It is formed at the radial axle of upside Radial dynamic pressure generating unit A1 of bearing surface pass through by mutual inclined in opposite directions and detached in the axial direction multiple dynamic pressure groove Aa1, Ab1 is constituted so that chevron shape arranges, in addition, radial dynamic pressure generating unit A2 being formed at the radial bearing surface of downside is passed through phase Mutually inclined in opposite directions and axially out multiple dynamic pressure groove Aa2, Ab2 are constituted so that chevron shape arranges.In upside Radial dynamic pressure generating unit A1 in, the axial dimension of the axial dimension of the dynamic pressure groove Aa1 of the upside dynamic pressure groove Ab1 than downside is big. On the other hand, in radial dynamic pressure generating unit A2 of downside, the axial chi of the dynamic pressure groove Aa2 of the upside and dynamic pressure groove Ab2 of downside Very little be equal to each other, and with constitute upside radial dynamic pressure generating unit A1 downside dynamic pressure groove Ab1 axial dimension equal.By This, is when rotary body 2 (axle portion part 21 and parts of bearings 22) rotates, the outer peripheral face 22a of parts of bearings 22 and the path of housing 7 The lubricating oil 11 being full of in gap (journal bearing gap) between inner peripheral surface 7a2 is by the thrust bearing of axial thrust bearing portion T Clearance side is pressed into.
In addition, in the embodiment described above, using being provided integrally with a portion 7a and closing this 7a The housing 7 of the bottom 7b of end opening, by be fixed on the inner peripheral surface of housing 7 (cylinder portion 7a) seal member 9 inner peripheral surface 9a Lai Form the seal clearance S that the upper end open to housing 7 is sealed, but as shown in figure 8, housing 7 can also be using independently The component of the bottom 7b of lower ending opening of setting cylinder portion 7a and closing this 7a.Correspondingly, in fig. 8, will be used for axle The sealing 7c and cylinder portion 7a that form seal clearance S between the outer peripheral face 21a in portion 21 are wholely set.It should be noted that also may be used This structure to be applied in the fluid dynamic-pressure bearing device 1 shown in Fig. 2.
In addition, in embodiment illustrated above, by with the housing 7 that motor base 6 is independently arranged be fixed on electronic The inner circumferential of machine pedestal 6, but the position (omitting diagram) being equivalent to motor base 6 can also be integrally provided on housing 7.
In addition, in embodiment illustrated above, in view of good the adding of the parts of bearings 22 being made up of porous plastid Work, forms radial dynamic pressure generating unit A, A1, A2 in the outer peripheral face 22a of parts of bearings 22, but radial dynamic pressure generating unit also may be used To be formed at the inner peripheral surface 7a2 of opposed housing 7.In addition, radial bearing portion can be by so-called many arc bearings, stepwise axle Hold and other hydrodynamic bearings known such as wave mode bearing are constituted.Similarly, thrust dynamic pressure generating unit B can also be not formed in On the lower surface 22c of parts of bearings 22, and it is formed on the inner bottom surface 7b1 of the housing 7 opposed with it.In addition, thrust bearing Portion T can be made up of other hydrodynamic bearings known such as so-called stepped bearing, wave mode bearing.
In addition, in embodiment illustrated above, by configuring rotor magnet 4 and stator coil 5 with staggering vertically, Thus having for by parts of bearings 22 and axle portion part 21 downwards in effect on the rotary body 2 including parts of bearings 22 grade The external force (magnetic force) of pressing (the opposing party is supported by thrust direction), for acting on the mechanism of rotary body 2 by this external force It is not limited to aforesaid way.Although omitting diagram, for example can pass through will be right in the axial direction with rotor magnet 4 for magnetic part Put configuration, so that above-mentioned magneticaction is in rotary body 2 (rotor 3).In addition, the thrust in the counteracting force as blasting action Very big, through in the case of just parts of bearings 22 can press downwards by this thrust it is also possible to omission as be used for by The magnetic force (magnetic attraction) of the external force that parts of bearings 22 presses downwards.
In addition, more than, to applying the present invention to be fixed with axle portion part 21 as rotary part, tool is vaned Situation in the fluid dynamic-pressure bearing device 1 of rotor 3 is illustrated, but the present invention also can be preferably applied to as rotation Part and being fixed with axle portion part 21 has the hub of disc installed surface, in the fluid dynamic-pressure bearing device 1 of polygonal mirror. That is, the present invention can not only be applied in this fan motor shown in Fig. 1 additionally it is possible to be preferably applied to be assembled in disc dress The spindle drive motor put, polygon scanner motor of laser printer (LBP) etc., other device for electric motivations In fluid dynamic-pressure bearing device 1 in.
Symbol description
1 fluid dynamic-pressure bearing device
2 rotary bodies
3 rotors (rotary part)
4 rotor magnets
5 stator coils
6 motor bases (holding member)
7 housings
7a sidepiece
7b bottom
7b1 inner bottom surface
8 access
9 seal members
10 axial gaps
11 lubricating oil
12 press-in portion
13 groove portions
21 axle portion parts
22 parts of bearings
22b upper surface (end face of axial opposite side)
22c lower surface (end face of axial side)
A, A1, A2 radial dynamic pressure generating unit
B thrust dynamic pressure generating unit
S seal clearance
R, R1, R2 radial bearing portion
T thrust bearing division

Claims (10)

1. a kind of fluid dynamic-pressure bearing device, it possesses：
The parts of bearings of rotary side, it is formed by porous material, and has end face in axial both sides；
The housing of Stationary side, it has bottom tube-like in what axial side was closed, and parts of bearings is contained in inner circumferential；
Seal member, it is arranged opposite with the end face of the axial opposite side of parts of bearings, makes the axial opposite side warp of parts of bearings From seal clearance to atmosphere opening；
Journal bearing gap, it is formed between the outer peripheral face of parts of bearings and the inner peripheral surface of housing；
Thrust bearing gap, it is formed between the end face of axial side of parts of bearings and the inner bottom surface of housing,
Journal bearing gap and thrust bearing gap are full of by lubricating oil, by being formed between journal bearing gap and thrust bearing The oil film of gap supports to parts of bearings in radial direction and thrust direction one side respectively,
Described fluid dynamic-pressure bearing device is characterised by,
It is folded with containing air between the end face and the end face of the seal member opposed with it of the axial opposite side of parts of bearings Axial gap,
The external force producing in the outside of housing acts on parts of bearings and parts of bearings is pressed on axial side, thus in thrust On the opposing party of direction, parts of bearings is supported.
2. fluid dynamic-pressure bearing device according to claim 1, wherein,
Described external force is the magnetic force producing between stator coil and rotor magnet, and described stator coil is arranged at including housing Stationary side, described rotor magnet is arranged at the rotary side including parts of bearings.
3. fluid dynamic-pressure bearing device according to claim 1, wherein,
Also there is press-in portion, described press-in portion when parts of bearings rotates by the lubricating oil in axial gap towards radially away from The direction press-in of seal clearance.
4. fluid dynamic-pressure bearing device according to claim 3, wherein,
Multiple groove portions that press-in portion is formed from the end face of axial opposite side of parts of bearings are constituted.
5. fluid dynamic-pressure bearing device according to claim 4, wherein,
The well width of each groove portion is gradually reduced towards the direction radially away from seal clearance.
6. the fluid dynamic-pressure bearing device according to claim 4 or 5, wherein,
Each groove portion has well width with the section shape being gradually reduced towards bottom land side.
7. fluid dynamic-pressure bearing device according to claim 1, wherein,
Seal clearance is formed between outer peripheral face and the inner peripheral surface of seal member of axle portion part, and the periphery of described axle portion part is fixed with Parts of bearings, described seal member and housing are wholely set or split setting.
8. fluid dynamic-pressure bearing device according to claim 1, wherein,
There is the dynamic pressure generating section making the lubricating oil in journal bearing gap produce dynamic pressure effect, this dynamic pressure generating section is by radially The shape of the lubricating oil axial thrust bearing clearance side press-in in bearing clearance.
9. fluid dynamic-pressure bearing device according to claim 1, wherein,
There is the access of the end face connection of the axial both sides making parts of bearings.
10. a kind of motor, possesses the fluid dynamic-pressure bearing device any one of claim 1 to 9.
CN201380031745.8A 2012-06-18 2013-05-22 Fluid dynamic bearing device and motor with same Active CN104411988B (en)

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